CN1470821B - Injector with throttle controllable nozzle and injection circulation using same - Google Patents
Injector with throttle controllable nozzle and injection circulation using same Download PDFInfo
- Publication number
- CN1470821B CN1470821B CN031450792A CN03145079A CN1470821B CN 1470821 B CN1470821 B CN 1470821B CN 031450792 A CN031450792 A CN 031450792A CN 03145079 A CN03145079 A CN 03145079A CN 1470821 B CN1470821 B CN 1470821B
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- Prior art keywords
- nozzle
- valve
- needle
- outlet
- throat
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- Expired - Fee Related
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
- F04F5/46—Arrangements of nozzles
- F04F5/461—Adjustable nozzles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3286—Constructional features
- B60H2001/3298—Ejector-type refrigerant circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0012—Ejectors with the cooled primary flow at high pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0013—Ejector control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Thermal Sciences (AREA)
- Jet Pumps And Other Pumps (AREA)
- Nozzles (AREA)
Abstract
An ejector (40) includes a nozzle (41) having therein a throat portion (41a), and a needle valve (44) that extends at least from the throat portion to the outlet of the nozzle. The needle valve is displaced in an axial direction of the nozzle to adjust an opening degree of the throat portion and an opening degree of an outlet of the nozzle. Therefore, even when a flow amount of refrigerant flowinginto the nozzle is changed, it can prevent a vertical shock wave from being generated by suitably adjusting both the opening degrees of the throat portion and the opening degree of the outlet of thenozzle. Accordingly, nozzle efficiency can be improved regardless of a change of the flow amount of the refrigerant.
Description
Technical field
The present invention relates to a kind of injector and its spraying cycle of use that has throttling adjustable nozzle, wherein can control two extent of opening of the outlet of throat and nozzle.Injector has the fluid pumping function, is used for coming circulation of fluid by the transmission fluid that carries high velocity jet.
Background technology
In spraying cycle, the pressure that sucks the cold-producing medium of compressor increases by in injector expansion energy being converted to the pressure energy, has reduced the power that compressor consumed thus.In addition, cold-producing medium circulates by the pumping function that uses injector and enters in the evaporimeter of spraying cycle.Yet when the energy conversion efficiency of injector, that is, when ejector efficiency reduced, the refrigerant pressure that is pumped to compressor can not increase by injected fully device.In this case, the power that compressor consumed reduces unsatisfactorily.On the other hand, the throttling degree of nozzle (access portal degree) is fixed in injector.Therefore, when the number change of the cold-producing medium of flow nozzle, nozzle efficiency and ejector efficiency change according to the variation of refrigerant flow.Wherein, when the pressure energy in the nozzle changed into the speed energy, nozzle efficiency was the energy conversion efficiency of nozzle.
In addition, according to the experiment that the present inventor did, as long as the opening degree simple change of the throat of nozzle, then the vertical vibration ripple produces between the outlet of throat and nozzle, and the pressure of cold-producing medium changes rapidly between them.Therefore, in the outlet of nozzle, fluid (cold-producing medium) is to be in subsonic state, and is consumption state.Therefore, cold-producing medium constant entropy state in nozzle can not reduce pressure, and nozzle efficiency can reduce widely.
Summary of the invention
Consider the problems referred to above to the purpose of this invention is to provide a kind of injector, its no matter the flow size of cold-producing medium can increase nozzle efficiency fully.
Another object of the present invention provides a kind of spraying cycle of using this injector.
According to the present invention, injector comprises that nozzle and pressure increase part, described nozzle is used for definite passage wherein, transmit fluid and flow through described passage, increase part at described pressure, fluid is sucked and mixes with transmission stream from nozzle ejection by taking away from the transmission fluid injection stream of nozzle ejection.In this injector, nozzle comprises throat, and this throat has on the passage of nozzle minimum cross section, and is provided with and regulates parts not only to regulate the opening degree of throat but also to regulate the opening degree of the outlet of nozzle.Because the opening degree of the outlet of the opening degree of throat and nozzle can be by regulating component controls,, still can limit the generation of vertical vibration ripple effectively even therefore when the changes in flow rate of the transmission fluid of flow nozzle.Therefore, can prevent to cause super swelling state, at described super swelling state, the transmission flow rate of fluid in the exit of nozzle becomes subsonic speed.Therefore, the flow size of the transmission fluid of flow nozzle no matter, nozzle efficiency can fully increase.
Preferably, regulate parts and comprise needle-valve, described needle-valve extends to the outlet of nozzle at least from throat.Therefore, the opening degree of the outlet of the opening degree of throat and nozzle can both be easily simultaneously controlled.Usually, needle-valve be arranged in nozzle axially on can move, and exceed the end of the outlet of described nozzle.
Injector of the present invention can be suitable for spraying cycle, and described spraying cycle comprises compressor, and it is used for compression and discharging refrigerant; First heat exchanger, the cold-producing medium that it is provided for freezing and discharges from compressor; Gas-liquid separator, it is used for cold-producing medium is separated into gas refrigerant and liquid refrigerant from injector, with second heat exchanger, it is provided for evaporating the liquid refrigerant in the gas-liquid separator. in this case, cold-producing medium in first heat exchange is depressurized in nozzle, and the cold-producing medium that is evaporated in evaporimeter is sucked up to the pressure increase part of injector. when the pressure that increases the part cold-producing medium at pressure increases, cold-producing medium from nozzle increases partially mixed with the cold-producing medium that comes flash-pot at pressure. therefore, when nozzle efficiency can improve, also can carry out spraying cycle.
Description of drawings
Other purpose of the present invention and advantage find out with reference to accompanying drawing is easier from following detailed description of the preferred embodiments, wherein:
Fig. 1 is the schematic diagram of explanation according to the spraying cycle of the preferred embodiments of the invention;
Fig. 2 A is the schematic section of explanation according to the injector of this embodiment; The signal enlarged drawing of the part of the nozzle of the injector of key diagram 2A during Fig. 2 B;
Fig. 3 is the Mollier curve (p-h curve) of explanation relation between refrigerant pressure and the enthalpy in spraying cycle;
Fig. 4 is a view of explaining the problem in the Comparative Examples;
Fig. 5 is the curve map of explanation nozzle efficiency in the present invention and Comparative Examples.
The specific embodiment
Below, with reference to accompanying drawing the preferred embodiments of the invention will be described.
In embodiments, the injector of spraying cycle typically is used as air-conditioning equipment.In the spraying cycle shown in Figure 1, fluorocarbon (fleon, 134a) or carbon dioxide etc. can be used as cold-producing medium.In spraying cycle, compressor 10 is by power suction and compressed refrigerant from vehicle motor obtained.Control compressor 10 discharge capacity (discharge capacity) to such an extent as to the temperature of evaporimeter 30 or pressure in preset range.The cold-producing medium that radiator 20 gives off from compressor 10 with cooling is set.Particularly, radiator 20 is hp heat exchangers, and it carries out heat exchange between cold-producing medium that flows out from compressor 10 and extraneous air.
Evaporimeter 30 is set with the evaporating liquid cold-producing medium.Particularly, evaporimeter 30 is low pressure heat exchangers, and it makes liquid refrigerant evaporates by absorb heat from air flowing.Therefore, the air that flows through evaporimeter 30 is cooled, and the air that has freezed can blow into compartment with the chilling room compartment.
The cold-producing medium of evaporation makes simultaneously and flow out cold-producing medium decompression and expansion from radiator 20, and increases the pressure of cold-producing medium so that its suction compressor 10 by expansion energy being changed into pressure energy in the injector 40 suction evaporimeters 30.
Gas-liquid separator 50 is separated into gas refrigerant and liquid refrigerant to the cold-producing mediums from injector 40, and stores the cold-producing medium that has separated there.Gas-liquid separator 50 comprises the gas-refrigerant outlet of the aspiration end that is connected to compressor 10 and is connected to the liquid-refrigerant outlet of the entrance side of evaporimeter 30.Choke valve 60 is arranged on the coolant channel between the entrance side of the liquid refrigerant outlet of gas-liquid separator 50 and evaporimeter 30, therefore, makes the liquid refrigerant decompression that is supplied to evaporimeter 30 from gas-liquid separator 50.
In spraying cycle, reference number C1-C9 shown in Figure 3 has illustrated the refrigerant condition of the position that reference number C1-C9 shown in Figure 1 when carbon dioxide is used as cold-producing medium is represented respectively.
Secondly, with reference to Fig. 1,2A and 2B describe the structure of injector 40 in detail. as shown in Figure 2, injector 40 comprises nozzle 41, mixing portion 42 and diffuser 43. nozzles 41 can convert the speed energy to by the pressure at the following high-pressure refrigerant of state of constant entropy and make from the high-pressure refrigerant decompression of radiator 20 and expand. and the gas refrigerant of evaporimeter 30 is pumped to mixing portion 42 by the high velocity stream of the cold-producing medium that sprays from nozzle 41, and the gas refrigerant that has aspirated mixes in mixing portion 42 with the cold-producing medium that has sprayed. diffuser 43 increases the pressure of cold-producing medium by the speed power conversion of cold-producing medium being become the pressure energy of cold-producing medium, simultaneously gas refrigerant that is aspirated from evaporimeter 30 and the refrigerant mixed of being sprayed from nozzle 41.
In mixing portion 42, to such an extent as to mix the power of the cold-producing medium from nozzle 41, sprayed and two kinds of cold-producing mediums streams of the cold-producing medium that from evaporimeter 30, is aspirated and be saved.Therefore, the static pressure of the cold-producing medium in mixing portion 42 has also increased.Because the sectional area of coolant channel increases gradually in diffuser 43, the dynamic pressure of cold-producing medium is converted into the static pressure of cold-producing medium in the diffuser 43.So refrigerant pressure all increases in mixing portion 42 and diffuser 43.Therefore, in this embodiment, pressure increases the structure that part has mixing portion 42 and diffuser 43.In theory, in injector 40, be saved in mixing portion 42 to such an extent as to the refrigerant pressure in mixing portion 42 increases the total output of two kinds of cold-producing mediums streams, to such an extent as to and the energy that refrigerant pressure further increases cold-producing medium in diffuser 43 in diffuser 43, preserve.
In this embodiment, electric actuator (for example linear magnetic plug motor and the stepping motor that comprises screw mechanism) is used as actuator 45.And the pressure of high-pressure refrigerant detects by pressure sensor (not showing).Then, regulate the extent of opening of the dilation 41b outlet of the extent of opening of spout 41a and nozzle 41 by needle-valve 41, to such an extent as to become goal pressure by the pressure that pressure sensor detected, described goal pressure is based on temperature that temperature sensor detected and determine.Temperature sensor is arranged on the high-pressure side to detect the temperature at spraying cycle mesohigh side cold-producing medium.Set target pressure is so that the coefficient of spraying cycle is maximum with respect to the refrigerant temperature of spraying cycle mesohigh side.As shown in Figure 3, when carbon dioxide is used as cold-producing medium, the critical pressure height of the pressure ratio cold-producing medium of high-pressure side cold-producing medium.In this case, to such an extent as to the pressure of the cold-producing medium of the aperture area flow nozzle of the coolant channel of control nozzle 41 is equal to or higher than critical pressure.On the other hand, when the pressure of the cold-producing medium of flow nozzle was lower than the critical pressure of cold-producing medium, the aperture area of the coolant channel of control nozzle 41 was so that the cold-producing medium of flow nozzle 41 has predetermined degree of supercooling.
In this spraying cycle, cold-producing medium is compressed in compressor 10, and be disposed to the cold-producing medium that radiator 20. discharges in radiator 20, be cooled from compressor 10, and usually in decompression in the nozzle 41 at injector 40 under the state of constant entropy. the flow velocity of cold-producing medium is increased to the velocity of sound that is equal to or higher than nozzle 42 exits in the nozzle 41 at injector 40, and the mixing portion 42. of inflow injector 40 in addition, institute's vaporized gas cold-producing medium is sucked the mixing portion 42 that enters injector 40 by pumping function in evaporimeter 30, described pumping function is to produce owing to taking away the high speed cold-producing medium that flows into mixing portion 42 from nozzle 41. cold-producing medium that is aspirated from evaporimeter 30 and the cold-producing medium that is sprayed from nozzle 41 mix in mixing portion 42, and the dynamic pressure of cold-producing medium is converted to after the static pressure of cold-producing medium in diffuser 43, flow into gas-liquid separator 50. therefore, the low-pressure side cold-producing medium is successively by choke valve 60, the pressure of evaporimeter 30 and injector 40 increases part and is circulated to gas-liquid separator 50. from gas-liquid separator 50
In desirable nozzle 41, the cold-producing medium of flow nozzle 41 from the inlet of nozzle 41 when the throttling part 41a by throttling, and increase towards the flow velocity of throttling part 41a cold-producing medium from the inlet of nozzle 41.Then, at throat 41a place, cold-producing medium is in critical condition, and flow velocity is Mach (Mach) 1.Cold-producing medium boils cold-producing medium and at dilation 41b place it is expanded by after the 41a of throat, and the flow velocity of cold-producing medium surpasses Mach1. at the dilation 41b place of nozzle 41
Yet in the cold-producing medium circulation of reality, the refrigerant flow of flow nozzle 41 changes according to air conditioning load.Therefore, usually, the outlet that is provided with and makes the dilation 41b of the channel cross-section of the 41a of throat and nozzle 41 based on the maximum stream flow in the maximum air conditioning load, and when refrigerant flow reduced owing to the air conditioning load that has reduced, the extent of opening liquid of the 41a of throat was reduced.In Comparative Examples shown in Figure 4, when the changes in flow rate of cold-producing medium, only the opening degree of throat 41 is controlled, because the opening degree of the outlet of nozzle 41 is fixed, the outlet that the pressure of the dilation 41b place cold-producing medium around the outlet of dilation 41b is lower than dilation 41b is the pressure of the cold-producing medium of nozzle 41 outsides on every side.Therefore, the vertical vibration ripple is easy to generate, and becomes the subsonic speed state at the flow velocity of the cold-producing medium in the exit of nozzle 41, and cold-producing medium is in the overexpansion of the exit of nozzle 41.So in this Comparative Examples, cold-producing medium is not decompression under the constant entropy situation in nozzle 41, and along with the minimizing of the flow of cold-producing medium in the nozzle 41, nozzle efficiency reduces widely, as shown in Figure 5.
According to the present invention, be arranged on needle-valve 44 on the coolant channel in the nozzle 41 and extend to the outlet (downstream end) of nozzle 41 at least.Therefore, by nozzle 41 axially on the moving of needle-valve 44, the opening degree of the opening degree of locating to export of the 41a of throat and nozzle 41 outlets can both be controlled.Therefore, even when the flow of the cold-producing medium of flow nozzle 41 changes on usable floor area shown in Figure 5 usually, can remain on about maximum to nozzle efficiency by the opening degree of locating to export of the control 41a of throat and the opening degree of nozzle 41 outlets, as shown in Figure 5.In Fig. 5, P1 has illustrated a kind of state, under this state, carries out refrigerating operation with high bearer rate in conditioner.That is, P1 has illustrated big cooling load state.
In the present invention, regulate the opening degree of locating to export of the 41a of throat and the opening degree of nozzle 41 outlets, in nozzle 41, produce to such an extent as to can prevent the vertical vibration ripple by needle-valve 44 and actuator 45.Therefore, can prevent that cold-producing medium is owing to the subcritical flow in the exit of nozzle is in the overexpansion state.
Though in conjunction with preferred embodiment the present invention has been described fully, should be noted that concerning the people that those are skillful to this multiple variation and modification will become significantly with reference to accompanying drawing.
In the above-described embodiment, the present invention typically is applied in the vehicle air conditioning equipment.Yet the present invention can be applied to (for example heater of refrigerator, freezer unit and water) in the another kind of spraying cycle.Actuator 45 can be to use the mechanical actuator of inert gas pressure or use the electric actuator of the non-electromagnetism of piezoelectric element).For example, electric actuator is stepping motor or linear solenoid motor.
In the above-described embodiment, by the single needle-valve 44 that uses actuator 45 to be controlled, the opening degree of the opening degree of locating to export of the 41a of throat and nozzle 41 outlets is simultaneously controlled.Yet, in the present invention, can provide the valve of the opening degree of locating to export of controlling the 41a of throat and the valve of the opening degree that control nozzle 41 exports independently.Even in this case, the opening degree of opening degree of locating to export by controlling the 41a of throat aptly and nozzle 41 outlets, the decompression degree of nozzle 41 can be conditioned aptly, and nozzle efficiency can improve effectively.
Should be appreciated that variation and modification in the determined scope of the invention by appending claims.
Claims (14)
1. injector comprises:
Nozzle (41), this nozzle are used for limiting therein a passage, and power transmitting fluids flows through described passage, and this nozzle comprises throat (41a), and described throat (41a) has cross-sectional area minimum in the coolant channel of nozzle (41);
Pressure increases part (42,43), wherein fluid by take away from the transmission fluid injection stream of nozzle ejection be inhaled into and with mix from the power transmitting fluids that nozzle ejected; With
Regulate parts
It is arranged to not only regulate the extent of opening of throat (41a) but also the extent of opening of regulating the outlet of nozzle.
2. injector according to claim 1 is wherein regulated parts and is comprised needle-valve (44), and described needle-valve (44) extends to the outlet of nozzle at least from throat.
3. injector according to claim 2, wherein needle-valve be arranged to make its nozzle axially on can move, and exceed the end of the outlet of described nozzle.
4. according to each described injector in claim 2 and 3, wherein:
Nozzle further comprises the dilation (41b) in throat downstream; With
Needle-valve extends to the outlet of dilation at least.
5. injector according to claim 1, wherein:
Regulate parts and comprise needle-valve (44), described needle-valve (44) extends to the outlet of nozzle at least from throat; With the actuator that is used for mobile needle-valve (45).
6. injector according to claim 5, wherein needle-valve extends to the outlet of nozzle at least from the inlet of nozzle.
7. injector according to claim 1, wherein:
Described adjusting parts comprise needle-valve (44), mode longshore current body direction nozzle that described needle-valve is given prominence to from the outlet of nozzle with the far-end of needle-valve extends to the outlet of nozzle at least from throat (41a), and actuator (45), described actuator is used to make described needle-valve to move along its axis, not only to regulate the extent of opening of throat (41a) but also the extent of opening of regulating the outlet of nozzle.
8. injector according to claim 7, wherein:
Described needle-valve (44) has second tapering part in the outlet that radially is arranged on first tapering part in the throat (41a) and radially is arranged on nozzle (41), and first tapering part and second tapering part form difformity.
9. spraying cycle comprises:
Be used to compress compressor (10) with discharging refrigerant;
First heat exchanger (20), the cold-producing medium that it is provided for freezing and discharges from compressor;
Injector (40), it comprises and is used to expand and the nozzle (41) of the cold-producing medium that comes from first heat exchanger stream of reducing pressure;
Gas-liquid separator (50), it is used for cold-producing medium is separated into gas refrigerant and liquid refrigerant from injector;
Second heat exchanger (30), it is provided for evaporating the liquid refrigerant in the gas-liquid separator, wherein:
Described nozzle has throat (41a), and this throat has cross-sectional area minimum in the coolant channel of nozzle; With
Injector comprises that further pressure increases part (42,43), the cold-producing medium that wherein comes flash-pot by take away from the cold-producing medium of nozzle ejection be inhaled into and with refrigerant mixed from nozzle ejected; With the adjusting parts
These adjusting parts are arranged to the extent of opening of not only regulating the extent of opening of throat but also regulating the outlet of nozzle.
10. injector circulation according to claim 9 is wherein regulated parts and is comprised needle-valve (44), and this needle-valve extends to the outlet of nozzle at least from throat.
11. injector circulation according to claim 9, wherein needle-valve is arranged in the axial removable extent of opening not only to regulate the extent of opening of throat but also regulate the outlet of nozzle of nozzle.
12., further comprise according to any one described injector circulation in the claim 9 to 11:
Actuator (45), this actuator be used for nozzle axially on mobile needle-valve.
13. injector circulation according to claim 9, wherein:
Described adjusting parts comprise needle-valve (44), mode longshore current body direction nozzle that described needle-valve is given prominence to from the outlet of nozzle (41) with the far-end of needle-valve extends to the outlet of nozzle at least from throat (41a), and actuator (45), described actuator is used to make described needle-valve to move along its axis, not only to regulate the extent of opening of throat (41a) but also the extent of opening of regulating the outlet of nozzle.
14. injector circulation according to claim 13, wherein:
Described needle-valve (44) has second tapering part in the outlet that radially is arranged on first tapering part in the throat (41a) and radially is arranged on nozzle (41), and first tapering part and second tapering part form difformity.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002199993A JP4120296B2 (en) | 2002-07-09 | 2002-07-09 | Ejector and ejector cycle |
| JP2002-199993 | 2002-07-09 | ||
| JP2002199993 | 2002-07-09 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1470821A CN1470821A (en) | 2004-01-28 |
| CN1470821B true CN1470821B (en) | 2010-05-05 |
Family
ID=29774540
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN031450792A Expired - Fee Related CN1470821B (en) | 2002-07-09 | 2003-06-27 | Injector with throttle controllable nozzle and injection circulation using same |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6966199B2 (en) |
| JP (1) | JP4120296B2 (en) |
| CN (1) | CN1470821B (en) |
| DE (1) | DE10330103A1 (en) |
| IT (1) | ITRM20030333A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109882453A (en) * | 2019-03-01 | 2019-06-14 | 一汽解放汽车有限公司 | The injector of variable cross section |
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| CN1291196C (en) * | 2004-02-18 | 2006-12-20 | 株式会社电装 | Ejector cycle having multiple evaporators |
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| CN100342187C (en) * | 2005-12-01 | 2007-10-10 | 上海交通大学 | Two-phase flow injector replacing refrigerator throttling element |
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| US20080115503A1 (en) * | 2006-11-16 | 2008-05-22 | Honeywell International, Inc. | Multi-port bleed system with variable geometry ejector pump |
| US20080118371A1 (en) * | 2006-11-16 | 2008-05-22 | Honeywell International, Inc. | Servo-controlled variable geometry ejector pump |
| US10101059B2 (en) * | 2007-11-27 | 2018-10-16 | The Curators Of The University Of Missouri | Thermally driven heat pump for heating and cooling |
| JP4760843B2 (en) | 2008-03-13 | 2011-08-31 | 株式会社デンソー | Ejector device and vapor compression refrigeration cycle using ejector device |
| JP4811493B2 (en) * | 2008-05-29 | 2011-11-09 | 株式会社デンソー | Ejector and manufacturing method of ejector |
| US20110113803A1 (en) * | 2009-05-14 | 2011-05-19 | Halla Climate Control Corp. | Multi-evaporation system |
| JP5338481B2 (en) * | 2009-05-26 | 2013-11-13 | 株式会社デンソー | Ejector |
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-
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-
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- 2003-06-27 CN CN031450792A patent/CN1470821B/en not_active Expired - Fee Related
- 2003-07-03 DE DE10330103A patent/DE10330103A1/en not_active Withdrawn
- 2003-07-07 US US10/614,361 patent/US6966199B2/en not_active Expired - Lifetime
- 2003-07-08 IT IT000333A patent/ITRM20030333A1/en unknown
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| CN109882453A (en) * | 2019-03-01 | 2019-06-14 | 一汽解放汽车有限公司 | The injector of variable cross section |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10330103A1 (en) | 2004-01-22 |
| ITRM20030333A0 (en) | 2003-07-08 |
| JP4120296B2 (en) | 2008-07-16 |
| CN1470821A (en) | 2004-01-28 |
| ITRM20030333A1 (en) | 2004-01-10 |
| JP2004044412A (en) | 2004-02-12 |
| US6966199B2 (en) | 2005-11-22 |
| US20040007013A1 (en) | 2004-01-15 |
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